Transmission



Febn 1, 1938. T, L, FAWICK 2,107,112

TRANSMISSION Filed Oct. 9, 1935 4 Shets-Sheet l vvef'or: Wwmas Z .Fad/01g Feb. 1, 1938. T. l.. FAwlcK 2,107,112

TRANSMISSION Filed oct. 9, 1935 4 Shets-Sheet 2 /75 /53 weg! 2455. Z

?? \\\m\ WMQMS Feb. 1, 1938. T. FAWlCK 2,107,112

TRANSMI SSION Filed Oct. 9, 1935 4 Sheets-Sheet 3 y www Patented Feb. 1,1938

TRANSMISSION Thomas L. Fawick, Akron, Ohio, assignor to Borg-Warner Corporation, Chicago, Ill., a corporation of Illinois Application October 9, 1935, Serial No. 44,135

14 Claims. (Cl. i4-332) My invention relates to transmissions for automotive apparatus.

While the particular device which I shall describe hereinafter in connection with the drawings is a heavy duty transmission adapted for use in motor busses, trucks and the like, it is to be understood that the invention is not limited to such uses but may be employed in all similar Work, for example, in connection with automobiles, locomotives and the like, and elsewhere as suitable or desired.

In transmitting the drive from a gasoline engine to the rear wheels or other driving wheels, it has become desirable to provide over-drive gear l5 means.

So far, there have been two general schemes for securing the desired overdrive-mst, by means of an overdrive gear device at the rear axle, and second, by means of an overdrive device at the :c-

celerating and reverse gear transmission between the engine shaft and the propeller shaft.

The rst scheme above mentioned has the objection of putting additional weight on the rear axle or connected parts. This results in high unsprung weight and is not desirable. The disadvantages of unsprung weight are so well known to engineers skilled in this art that no recapitulation of the same 'is necessary.

Furthermore, in all types of overdrive devices m, using conventional gearing, the overdrive is obtained entirely through tooth roll. 'I'hat is, if they obtained, say, 100% direct drive on third speed, then when shifted to the fourth speed, which we will say is geared up they would have all or 130% tooth roll. In fact, the tooth roll in such a device would be the same in principle as driving in second gear in the conventional three-speed transmission. This great tooth roll makes it commercially impossible to obtain a 4 quiet gear ratio in overdrive, and, as a result, de-

vices of this sort are noisy and are subject to considerable wear.

'I'he main object of the present invention is to provide a short, compact, heavy duty transmis- 45 sion, complete with four forward speeds, i. e., low, second, direct, and overdrive; also reverse; and to provide a transmission with synchronizing clutches on all ratios. 'This eliminates the usual necessity of shifting the gear teeth of one gear ,-,0 into mesh with the teeth of another gear and, thereby, the clashing of gear teeth, and enables the use of helical teeth throughout, which usually produce a noiseless or at least an exceptionally quiet transmission. y

55 e The present transmission, with overdrive incorporated, is considerably shorter than the conventional transmission having only three speeds where the same'gear teeth are used. Itis a common fact that the longer a crank case or gear case is made, the more liable it is to Weav- 5 ing or distortion. The useof an overdrive in the transmission has usually added considerable length. According to the present invention, I have taken a standard production three-speed transmission and have built in the overdrive so that it 10 takes vengine torque only. The gear case is considerably shorter than the regular three-speed transmission Without overdrive. This is due in l part to the arrangement of the synchronizing and positive clutches for low and second speeds, and 15 also the synchronizing and positive clutch means for reverse on the countershaft. These clutches are usually on the main through shaft where they must be very large and powerful. By providing the clutches for low', second and reverse on the 20 countershaft, it is possible to make these clutches -a great deal smaller and tov obtain the same synchronizing and clutching ability as has been obtained'with clutches two to three times larger mounted on the main through shaft. Also, by locating the synchronizing and positive clutches for low, second and reverse on the countershaft, these clutches may run in an oil bath in the transmission case, assuring ample lubrication to these clutches.' 30

For the purpose of compactness and reduced overall length, the driving shaft is preferably eX- tended through the internal overdrive gear and through the cooperating external internal gear and reaches over adjacent a direct drive driven 35 member which is disposed in proximity to a clutch part on the external internal gear and a splined driving connection with the driven shaft of the transmission and adjacent a synchronizing and clutching member for connecting the external 40 internal gear or the direct drive driven member to the driven shaft of the transmission selectively, as desired.

The driving shaft extends from the flywheel clutch bearing through the front Wall of the transmission case and into proximity to the rear wall of the transmission case, and its rear end is piloted in the forward end of the driven shaft of the transmission. This, with the other features to be hereinafter described, gives great compactness and particularly short over-all length. The driven shaft has improved bearing support.

According to the present invention, the driven shaft has a connected low ratio gear and splines which have permanent and slidable driving endrive, and are disposed inside the external teeth of the low ratio gear.

and provided with a second ratio' gear nxed endwise on the driven shaft and against rrelaftive'rota` tion with respect thereto. y rf' lv ;`1' Another feature resides in supportlng'the 'ex' engine to the rear axle, in' combination wii.lif,t l'i` synchronizing and clutching device forthe second* ratio gear on the countershaf't-.

It is to be understood' that tneinventi'oiisjnot limited to the particular' combinationfofnratio gear drives shown in the drawings;4

Further features and advantages of the y l tion will be apparent from thefollowing detailed description taken in connection` with the accompanying drawings, in which: I

Figure 1 is a longitudinal sectional {view of a.'

transmission embodying the present invention;

Figure 2 is a fragmentary detail section showing the synchronizing and clutching means for reverse drive and first ratio drive in reverse drive position; v

Figure 3 is a view similar to Figure 2 showing the synchronizing and clutching means for reverse drive and rst ratio drive infirst ratio drive position; f

Figure 4 is a fragmentary detail section showing the synchronizing and clutch means for second ratio drive in second ratio drive position;

Figure 5'ls a fragmentary section taken on the line 5 5 of Figure 1; f

Figure 6 is a fragmentary detail section taken on the line 6--6 of Figure 5;

Figure 7 is a fragmentary view showing the shifting fork for second ratio drive; and

Figure 8 is a longitudinal sectional view of another form of transmission of my invention.

Referring first to Figures 1 to 7,'inc1usive, the transmission is housed within a case 5 which is preferably mounted upon the vehicle frame, which frame, in turn, is preferably spring supported upon the rear axle as, for example, in the manner illustrated in my copending application Serial No. 10,769, tlled March 13, 1935.

The shaft 5 is the driving shaft and extends from the flywheel clutch bearing through the front wall 1 of the case 5 and into proximity to the rear wall 8 of the case. The rear end of the shaft 6 is piloted in the driven shaft 9 which is in the4 form of a forging having a tubular portion telescoping the rear end ofthe shaft 5 and provided with an integral or directly connected low ratio gear I0. Roller bearings provided at Il between the rear end of the shaft I and the shaft 9 are held endwise by a flange I2 andan annular shoulder I3 onthe shaft 5. A second ratio gear I4 is held endwise and splined at I5- upon the `driven shaft 9 adjacent the gear I0.

The shaft 9 is supported in the rear wall of the alom-1a invenfis adjustable by means of antadjusting ring 33 2 threaded upon the flange at the outer end of the sleeve and abutting kthe end of the closure mem- `v=-race of bearing I1.

main transmission case 5 and adjacent gear i4 by a bearing Il, and rearwardly of the bearing Il in a roller bearing I1. In the illustrated embodiment of the invention, a bevel driving pinion Il isjsplined at Il upon shaft 5 adjacent bearing yfil.- A bevel gear 2l meshes with pinion Il and constitutes' a power take-oi! for transmitting the drive v,obliquely as, for example, from a transverseengine to the rear axle used in Greyl "houndv-busses. This diagonal take-of! may be te'rnal internal gear by needle-pointbearings in tted `within the scope of the present invention, "where it is omitted a universal `loint may be edto the rear end of shaft 5 instead of em- 'ylbe'fsupported in a manner similar to that 15764; filed April 1l, i935.`

I1 is carried" by .a sleeve member 2i', which'sleeve member is mounted in a hub 22 formedintegral withva closure member 25 secured byl 'stud bolts 25tothe rear end of an auxililary 'enclosureI 28 'attached to the rear end of =,Can vmember 21 a cylindrical portion .2l which vnts into sleeve 2|, and the outerracev 2,5 of bearing 'I1 is heldbetween the inner end 'of this'cylindrical portion and an internal shoulder 3,0 within sleeve .22.

nuts 22 vthreaded upon their outer ends, clamp the cap 21 and sleeve'2Iv in place, and sleeve 2i v,iusting nut 36 is threaded upon the rearward end of shaft 9 and into engagement with the inner The gear 20 has a shaft supported in a bearing 31.

s vAt the forward end of case 5, internal gear 40 has a hub'portion splined at 4I upon shaft 5 within an opening in front wall 1. The gear 40 preferably has pressed flt on the splines 4l, and

the hub of this gear is supported in a bearing 42. Bearing 42 is carried in a sleeve member 43 having, at its inner end, a flange 44 abutting the inner end of the outer race of bearing 42, and, at its outer end, a flange 45 positioned between the front wall 1 and a casing part 46. Bea-ring cap f 41 has a partially cylindrical portion fitting into the sleeve 43 and abutting the forward end of the outer race of bearing 42, and a tubular portion 45, which extends forwardly along shaft 6 and is preferably provided internally with oil'trapping grooves 49. The shoulder 50 on gear 40 is clamped against the inner end of the inner race of bearing 42 by a nut 5I which cooperates with the outer end of the inner race of this bearing, there preferably being a washer 52 interposed therebetween. The vmounting of the internal gear 40 in bearingy 42 provides perfect alignment for the internal gear teeth, and, with the bearings at I6, I1, provides an admirable support for the parts in which quietness and a perfect pitch line circle are obtained.

'Ihe internal gear 4l has internal helical teeth 52 which mesh with external helical teeth 541on an external internal or composite gear ring 55. 'I'he external internal gear 55 is supported exshown'i ',iny'copending application Serial No.

Stud bolts 3|, havingployin'gfthe pinion Inl, in which case the shaft S ternally on needle-point bearings 56 in a cage 51 carried by a retainer ring 58 and held againstv load beyond the forward needle-point rollers and specifically within the internal drive gear.

It is desirable, from the standpoint of quantity production and maximum quietness of gear op,- eration, to make the internal teeth 58 and the cooperating external teeth 54 helical, and, in fact, all of the gears in the present transmission are preferably helical gears. Straight teeth are, however, contemplated within the scope of the present invention.

'Ihe internal helical teeth 60 on composite gear 55 mesh with external helical teeth 6| on a tubu lar overdrive member 82. This member 62 is mounted within composite gear 55 and needle'- point bearings 56 on needle-point bearings 68 on the driving shaft 8. The needle-point bearings 88 comprise two groups of small diameter pins or rollers separated endwlse by an external annular rib 84 on shaft 5 and held endwlse between this rib and shoulders 65 and 66 on shaft 8.

'Ihe driven member 68 for direct drive is splined at 68 on shaft 6 and is held against endwlse movement to the right (Figure 1) by a retainer ring '|0. A thrust vwasher 1| is interposed between the forward end of the hub of the direct drive member 88 and the adjacent end of the overdrive member 82 to take the thrust developed between'these parts by the helical gear teeth. The washer 1| is placed at this location so that it will have a low relative sliding speed, as for instance, if the internal gear has thirty-two teeth and the meshing spur gear has twenty-eight teeth, it is obvious that the unit will make seven complete revolutions before this washer gains one complete revolution on its sliding thrustface, i. e., this washer turns in accordance with the tooth difference.' Interposed between the radially extending portion at the right-hand end roi the member 62 and the adjacent end of the external internal gear member 55 is a thrust washer 14 positioned by pins '|5, and interposed between the forward end of external internal gear 55 and gear 40 is a thrust washer 16 positioned by pins 18.

The driven member 68 for direct drive is provided peripherally with external clutch teeth for engagement with internal clutch teeth 8| on the synchronizing and clutchirm ring 82 when this ring is shifted to the right from'neutral position, as shown in Figure 1. These same teeth 8| are adapted to be engaged, when the ring 82 is shifted to the left, with external clutch teeth 84 peripherally about the radially extending portion of the overdrive member 62.

The low ratio gear l0, formed integral with shaft 9, has external teeth 85, and internal splines 86 which are in permanent and slidable driving engagement with external splines81 on the adjacent end of the synchronizing andclutching ring 82. The splined engagement at 86, 81 is inside the external teeth 85 of the low ratio gear I0. A thrust washer is preferably interposed between the ring 'l0 and the adjacent portion of the gear |0.

The splines 8l are slidable with respect to the splines 86 in shifting member 82, and this slidable splined engagement is of sui'cient length for constant engagement when member 82 is in 'neutral position as shown4 in Figure 1, as well as when this member is shifted to engage the vteeth 8| with the teeth 80 and when said member 82 is shifted in the opposite direction to engage the teeth 8| with the teeth 84. The telescoping of the ruht-hand end of the member 82 within the external toothed portion of gear I0 makes for circumferentially spaced openings v exceedingly compact endwlse relation of these parts.

Rearwardly of the external clutch teeth 84 the overdrive member 62 is provided with a synchronizing sleeve 85 secured by rivets 86 thereon. Forwardly of the external clutch teeth 80 the direct drive member 88 is provided with a synchronizing sleeve 81 secured thereon by rivets 98. 'I'he sleeves 85 and 91 may be formed of cast bronze or other suitable material, and have oppositely conical external frictional clutch or synchronizing surfaces for synchronizing engagement with the oppositely conical synchronizing surfaces on a synchronizing ring 00.

Secured as by means of rivets or the like to the double-cone synchronizing member |00 is a ring |02. which is provided with a plurality of |03. The clutching ring 82 carries a plurality of studs |04 of hexagonal form as shown in Figures 1 and 6. These studs are held in place in corresponding openings in the clutching ring 82 in any suitable manner, as by means indicated more or less diagrammatically at |05, or in the manner shown in my copending application Serial No. 15,764, flied April 11, 1935. The studs |04 project inwardly from the ring 82 and into the openings |03 in the ring |02.

.The clutching ring 82 and synchronizing ring |00 are movable with respect to each other, but spring-pressed detent means is provided for causing the two parts to move together. Such detentmeans is disposed within the driving studs |04, and comprises a coiled spring |08 disposed in a recess in the associated stud and pressing a steel ball H0 into a groove ||2 formed in the outer surface of the synchronizing ring |00. The clutch ring 82 has limited rotative movement and is axially'slidable on the part |02 for engaging the teeth 8| with the teeth 80 for direct drive, or with the teeth 84 for internal gear overdrive.

The openings |03'in the ring 02 are especially formed as best shown in Figure 6. These openings are of approximately cruciform shape, and vare provided with generally semi-hexagonal intermediate recesses I I4 and 5 and laterally disposed recesses ||6 and I|8 of similar form but somewhat longer. The associated stud |04 is adapted to be disposed in any one of these recesses in the operation of the transmission, as will be apparent from the following description.

The clutching ring 82 has an external groove |20 for engagement with a shifter arm 2| secured upon a shifter rod |22. The shifter rod |22 is journaled at |23 and |24 in the top closure |25 for the case 5, and this rod |22 may be shifted manually or by air, or in any other suitable or desired manner. Movement ofV the rod |22 to the right shifts the clutch ring 82 to the right, and movement of the rod |22 in the opposite direction shifts the ring 82 in the oppo site direction.

In operation, the initial movement of the ring 82, for example, to the left (Figure 1) carries with it, due to the engagement of the spring-pressed ball ||0 in the groove H2, the double-cone synchronizing part |00. This causes the left-hand conical surface of this part to engage the conical surface of the ring 95, and as soon asthis engagement is effected, the rotation of the overdrive member 62 drags with it the parts |00 and A |02 until the stud |04 is engaged by the recess ||5. A s soon as this is accomplished, further shifting of the ring 82 to the left to engage the clutch teeth 8| with the clutch teeth 84 acts 4- through the'ensagement of the stud tu with the inclined surface at the lowerv side (Figure 6) of the recess tocarrywith ittheparts |33and |32. Thus, more forcible synchronizing engagement is obtained than of merely the springpressed ball I I0 were relied upon to press the synthronizing surfaces into ensssement.

The same'action is provided whenthe ring 32 is shifted in the opposite direction to engage'the internal clutch teeth Il Wlth'theexternal clutch the angle of the'sides of the recess 1|4 or ||3.A

When the parts are synchronized, the stud |34 slides off the inclined face of the recess ||4 or l I5, and the positive clutches are engaged. Ji- 'I'he second ratio gear I4, which is held endwise en the driven lshaft s and splined thereto,

. intocooperation with the rear end of the innerhas permanent driving engagement with the external helical teeth of a gear |30 rotatably mounted on the countershaft |32. The gear |33 is mounted on roller bearings |34, shown as of lthe 'Iimken. type, for the purpose of taking care of thrust loads developed by the helical gear teeth. Ihe'bearing at |34 makesA it unnecessary to use such a bearing on the main shaft. A gear -|36, rotatably supported on needle-point bearings |31 on the countershaft |32, has external helical teeth in permanent driving engagement with the teeth 35 of the low ratio gear I0. A washer |33, clamped in place against rotation between the rearward end of the gear |36 and the forward end of the forward inner race member of the bearing |34, takes the end thrust of the low ratio gear on forward driving operation of the vehicle. When the vehicle drives the engine, as for example, going down-hill, the end thrust of the gear |36 is taken by a thrust washer |40.

'I'he countershaft |32 is rotatably supported at its opposite ends in bearings |45 and |43, respectively. The bearing |45 is carried by bearing cap |41 secured at |43 to front wall 1 of case 5. The bearing |46 is carried by a bearing cap |49 secured to rear wall of case -5 by `bolts |50. The forward end of shaft |32 is reduced and piloted freely at |5| in bearing |45, and a nut |52 is threaded upon the rear end of Ashaft |32r and race of bearing |46. Bearing ',cap |40 includes .e seperate end plate m boned thereto at tu.

vor coaxial 'with respect to bearing |45;-

'I'he internal gear 40 has external helical teeth outside and atv least in partial `transverse ment upon countershaft |32, and has external teeth. |12 in permanent sliding engagement with the internal, teeth |13 of the outer positive clutching ring |14. 'Ihe ring |14 has a groove |15 whereby it may be operated by .the same shift lever which shifts the synchronizing and clutching means for second ratio drive. overdrive, and

.direct drive, or votherwise as. suitable or desired. splined washer |13 is -grooved for application over splines |1| and is then turnedto interlock with the splines against endwise removal. "The synchronizing and clutching member |33for low This permits grinding vofthe helical teeth of gear |33 without interference by the member |33.l i

Rearwardly of its external teeth, gear |64 has ratio drive is separate fromand splined upon .gear |33 at |3|.

integr-ex. eluten teethV m, and rearwardly er these teeth is a synchronizing sleeve |33 riveted at |34 upon the tubular. rearward end of gear |34. Sleeve |33has aconical outer surface, andv riveted at |33 upon memberlll is `a'synchroniz- 'ing sleeve |31 having an oppositely conical outer surface. The sleeves |63 and |31 may be formed of cast bronze or other suitable'v material; The

synchronizing ring |10 hasA` oppositely conicalv .|14 to move on past the ring |10 for engagement of the clutch teeth |13 with the clutch teeth |62 for reverse drive, or engagement of the clutch teeth |13 with clutch teeth |92 on member |30 for low ratio drive. In the neutral position of ring |10 as shown in Figure l, there may be .a

slight clearance between the cone clutch surfaces.

The garter spring |90 is preferably made of spring wire. It may be of square section with the sides flared inwardly slightly, as set forth in my copending application, Serial No. 15,764, flied April 11, 1935, so that as the wireis wound to the desired form, the stretch along the outer periphery of the convolutions thereof will bring the section of the wire to `substantially square or rectangular form. The turns of the spring may be wound relatively close together, and the ends of the garter spring` |90 are suitably joined together. This spring encircles the synchronizing ring |10 and lies in an annular'groove |95 formed about the teeth |12.` The clutching ring |14 has an internal groove |96 which, whenregistered with groove |95, is 4adapted to receive the outer portion of the garter spring |90 which expands outwardly intothe groove |96 andv yieldingly connects the two. rings.

'I'he sides of the groove |36 flare inwardly, and as the synchronizingv ring |12 is engaged, for

. example, with the conical surface of the member |33 in the movement of the ring |14 to the left (Figure 1), continued movement of the member |14 in this direction will cause the right hand Aside of the groove |96 to force the garter spring |90 vinwardly into the groove |95 and from the groove |96 so that the member |14 may vcontinue its movement to engage the clutch teeth |12 with the clutch teeth |62 without further movement of the synchronizing ring |10. In shifting into low ratio drive, the action of the garter spring against the opposite side of the groove |96 is the'same. .Figure 2 shows the position of the parts after the gear |84 has been synchronized -with the ring |10, and the clutch teeth |12 engaged with the clutch teeth |82 for reverse drive. Figure 3 shows the position of the parts after the member |80 and low ratio gear |36 have been synchronzied with the ring |10 and the clutch teeth |12 moved into engagement with clutch teeth |92 for low ratio drive. It is to be understood that the synchronizing and clutching means for overdrive and direct drive have a neutral position, as shown in Figure 1.

'I'he second ratio gear |30 is provided rearwardly of its external teeth with integral clutch teeth 200, and rearwardly of these teeth 200 is a synchronizing sleeve 20| riveted at 202 upon the tubular rearward end of gear |30. A ring 203 is splined at 204 upon countershaft |32, and a synchronizing ring 205 is slidably splined at 206 upon ring 203. The ring 205 has external clutch teeth 201 which engage slidingly with internal clutch teeth 208 in the positive clutching ring 209 for low ratio drive. This ring 209 has clutch teeth 2|0 for engagement with clutch teeth 200 when ring 209 is shifted to the left from neutral position, as shown in Figure 1, and ring 205 has an internal conicalclutch surface 2|| for synchronizing engagement with external conical surface of sleeve 20| for synchronizing gear |30 with respect to ring 205 ahead of positive clutching engagement of ring 209 with clutch teeth 200.

A coiled garter spring 2|5 yieldingly connects the synchronizing ring 205 to the clutching ring 209, so that the ring 205 will move yieldingly with the ring 209, and, after the two parts |30 and 205 are synchronized by engagement of the clutch surface 2| 0 with the synchronizing sleeve 20|, permits the ring 209 to move on past ring 205 for engagement of the clutch teeth 2|0 with the clutch teeth 200 for low ratio drive. When the ring 205 is out of synchronizing engagement with the sleeve 20|, there may be a slight clearance between the cooperating conical surfaces.

The garter spring 2|5 is similar to the garter spring |95. This spring encircles the synchronizing ring 205 and lies in an annular groove 2|6 formed about the teeth 201. The sides of the groove 2|6 iiare outwardly, and the clutching ring 209 has an internal groove 2|8 to receive the outer portion of the garter spring which yieldingly connects the two parts, as shown in Figure 1. As the synchronizing ring 205 is engaged with the conical surface of the sleeve 20| in the movement of the ring 209 to the left (Figure 1), continued movement of the member 209 in this direction will cause the left hand side of the 4groove 2|6 to expand garter spring 2|5 outwardly into groove 2|8 in ring 209 and from the groove 2|6, so that the member 209 may continue its movement to engage the clutch teeth 2|0 with clutch teeth 200 without further movement of synchronizing ring 205. Figure 4 shows theposition of the parts after the gear |30 has been synchronized with respect to the ring 205 and clutch teeth 2|0 engaged with clutch teeth 200 to connect gear |30 positively to countershaft |32.

The ring 209 has a groove 220 for engagement by a shifter'fork 22| (Figure 7) for second ratio drive. This shifter fork may be operated from the same shift lever which operates the synchronizing and clutching devices for the other gears, or otherwise as desired. The gears |4 and |30 may be provided with lateral oil feeding ducts, indicated at 225 in Figure 1.

It is believed that the operationvof the device will be apparent from the foregoing description. With the parts in the position shown in Figure 1, the transmission is'in neutral. I n order to obtain low ratio drive, the ring |14 -is shifted rearwardly. This rearward movement of the ring |14 moves the synchronizing ring with it Iuntil the low ratio gear |36 is synchronized with respect to the countershaft |32, whereupon the internal teeth of the ring |14 engages the teeth |92 and positively connects the gear |36 to the countershaft. The drive is then transmitted from drive shaft 6 through meshing gears 40 and |62, countershaft |32 and meshing gears |36 and |0, to drive the driven shaft 9 at low speed. Second ratio is obtained by shifting ring 209 forwardly, the engagement of the friction surface 2|0 of the ring 205 with the cooperating friction surface of the sleeve first synchronizing the gear |30 with respect to the countershaft, whereupon the internal clutch teeth 2|0 move into positive clutching engagement with the teeth 200. Secondl ratio drive is then transmitted from the drive shaft 6 through the gears 40 and |62, counterlshaft |32, and meshing gears |30 and I4, tothe driven shaft 9.

In order to obtain direct drive, the clutching ring 82 is shifted rearwardly, the cooperating friction surfaces first synchronizing the ring 82 with respect to the direct drive member 68, whereupon the internal clutch teeth 8| are moved into positive clutching engagement with the clutch teeth 80. Direct drive is then transmitted from the drive shaft 6 through the direct drive member 68, clutching ring 82, and gear |0, to the driven shaft 9. Internal gear overdrive is obtained by shifting the ring 82 forwardly from the position shown, the cooperating friction surfaces rst synchronizing this ring with respect to the overdrive member 62, whereupon the internal clutch teeth 8| are positively engaged with the clutch teeth 84. Internal gear overdrive is then transmitted from the drive shaft 6 through the internal gear teeth 53, and the meshing external teeth of composite gear 55, and thence through the internal teeth of the composite gear and the meshing external teeth of the overdrive member 62, Ato the clutching ring 82, and through the low ratio gear I0 to the driven shaft v9.

The transmission may be lubricated by an oil bath (not shown) within the case 5, and a drain plug may be provided at the bottom as shown at 230. By providing the clutches for low, second and reverse on the countershaft, these clutches may run in the oil bath, thereby assuring ample lubrication to the synchronizing clutches at all times. Furthermore, as already pointed out, by providing the clutches for low, second and reverse on the countershaft, it is possible to make these clutches a great deal smaller and to have the same synchronizing ability as clutches two or three times larger mounted onV the main shaft. synchronizing clutches are provided on all ratios, thereby eliminating the usual necessity of shifting gear teeth of one gear into the gear teeth of another, and eliminating the clashing of gear teeth and making it possible to use helical teeth throughout.

The absence. of shifting gears along the main shaft and the provision of but one shiftable synchronizing and clutching device for direct drive and overdrive along the main shaft with the syn- V chronizing and clutching devices for low ratio,

second ratio, and reverse, along the countershaft, provides a transmission with overdrive incorporated which is considerably shorter than the conventional transmission having only three speeds where the same gear tooth is used. The

use of an overdrive in the transmission, as heretofore. usually mea'nt considerably added length, which I` avoid, and the liabilityto weaving` or distortion isreduced.

The device shown in Figure 8 .is anv overdrive device for use in connection with the vusual acoelerating and reverse gear transmission enclosed within the usual case 218. 'Ihe shaft 218 is the usual driven shaftof the transmission housed within casev 8. Therear end of this shaft is reduced, and this reduced end projects into the case 211 for the overdrive device. and has piloted therein the reduced forward lend of the driven shaft 218 of the overdrive device. An internal gear 219 is splined at 288 upon the reduced end-'of Ashaft 218 land is supported in a bearing` 28|. The bearing 28|, in turn, is supported by a lbearing retainer 282 held in the opening 288 in the rear end wall 284 of case 218 andagainst endwise movement by flange 288 clamped between the two I casings 218 and 211. 'I'he end of case 211 which split for application to the outer race of bearing 28|, and this ring takes the end thrust of the helical teeth in the internal gear drive.

The internal gear 218 has internal helical teeth 288 which mesh with external helical. teeth 288 on an external internal or composite gear 298, the opposite end of which is provided with internal helical teeth 29|. The external internal' gear ring 288 is supported in a bearing 292 mounted in the relatively short forward portion 211a ofy the case 211. The outer race 288 of bearing 292,V is held endwise between a shoulder 284'in forward portion 211a of case 211, and a centering flange 298 integral with the forward end of rear portion 211b of case 211 and fitting telescopically into the rear end of case portion 211a. The rear case portion 211b is clamped to forward case portion 211a by bolts 288, and case 211 is suitably attached to the rear end of case 218.

'I'he internal helical teeth 29| on external internal gear 298 mesh with external helical teeth 291 on an overdrive member 298. This member is preferably mounted on needle-point bearings 299 Aon tubular direct drive member 888 which extends through overdrive member 298 and external internalgear 298 and is splined` at 88| to the reduced end of shaft 218. Interposed' between the lateral enlargement at the rear end of direct drive member 888 and the adjacent en d of overdrive member 298 is a thrust'washer 882,

and another thrust washer 884 is interposed tween flange 888 of overdrive membe`r1288 v'and the adjacent end of external internal gear 298. The reduced end of driven shaft 218, which is piloted in the end of shaft 218, may be provided with a suitable lbushing/as indicated at 888.

The direct drive member 8881s provided peripherally at its right-hand end (Figure 8) with external clutch teeth 888 for engagement with internal clutch teeth 889 on a shiftable clutch ring 8|8 when this ring is shifted to the right from the neutral position illustrated. 'Ihese same teeth 889 are adapted to be engaged when ring 8|8 is shifted to the left (Figure 8) withexternal 'clutch teeth 8|| on the overdrive member 298.

The driven shaft 218 has an intel'al nange 8|2 provided peripherally with external splines 8|4 which engage internal splines 8|8 inJthe right.

teeth8l4 when member 8|8 is shifted to engage theteeth 888 with the teeth 888 andwhen saidv member 8|9 is shifted in the opposite direction to engage the teeth 889 with the teeth 8| -The -teeth8i8 beinglarger than the'teeth 888 permit the teeth 8 8 to move telescopicaily over the teeth 888 in'shifting the member 8|8 to engage teeth )n with the teeth :l i. This is important in that it permits the rear bearing 828 to be brought up close to the direct drive member 888 without interference between teeth 8|8 and teeth ,888'.

lWhen member 8 |8 is shifted to the left (Figure 8);.

the teeth 8|8 move over the teeth 888 clear of the same so that therewill be no interference between .these parts and, at the same time, the overlapwith respect to the -isf thrust washer 824 is interposed between the inner race of the bearing 828 and the worm gear 82|.

VThe rearward end of casing portion 211b'is pref` erably provided with a fluid-tight oil ca p or' closure device, indicated more -or lessv diagram matieeiiy and in its entirety at 32s. vThis device f seals the rear end of the casing for the overdrive gear device against the escape of lubricant which is maintained 'at the desired level within the casing. 'I'his device, of course, cooperates to this end with the means'for connecting the splined endfof shaft 218 to the propeller shaft.

lThe member sin is shifted in ahy suitable or desired manner, as by means of a shifter' rod 888 slidable in `the upper portion of the casing part 211b. The rod 888 has a shifter arm88| secured thereto, and this arm has .suitablev shifting engagement or cooperation f with an external groove 884 in the member 8|8. A spring-pressed ball member 888 cooperates with notches 888 to rev tain roja min the positions in which the clutch teeth" 889 are *engaged*v with the teeth .888 and In thl'ribdimen't 0f the invention illustrated ".inll'igurel, a v'snap washer is preferably provided at 488 for the purposeof holding the shaft 8 end# wise when the direct drive clutch at 91 is engaged. v

' I have described the invention in connection with the details of particular devices, but I do not between the driving and driven shafts'and ar- 75 ranged on the driven shaft in coaxial relation with respect thereto, meshing 'gears connecting the drive shaft and countershaft, low ratio and second ratio gears fixed endwise on the driven shaft and against rotation with respect to said driven shaft, low ratio and second ratio gears rotatable freely on the countershaftv and in constant meshing engagement with the low ratio and second ratio gears on the driven shaft, a reverse gear rotatable freely on the countershaft and operatively connected with ,said driven shaft, shiftable means on the countershaft for positively clutching said low ratio and second ratio countershaft gears selectively to said countershaft and for freeing same therefrom, and shiftable clutch means also on the countershaft for positively clutching said reverse gear to said countershaft.

2. A gear set for motor vehicles having in combination, a driving shaft, a driven shaft, a countershaft, overdrive and direct drive means between the driving and driven shafts, meshing gears connecting the drive shaft and countershaft, low ratio and second ratio gears fixed endwise on the driven shaft and against rotation with respect to said driven shaft, low ratio and second ratio gears rotatable freely on the countershaft and in constant meshing engagement with the low ratio and second ratio gears on the driven shaft, ,a reverse gear rotatable freely on the countershaft, synchronizing surfaces and positive clutch teeth one said low ratio and second ratio countershaft gears and on said reverse gear, a synchronizing ring shiftably splined on the countershaft between said reverse and low ratio countershaft gears and having synchronizing surfaces engageable selectively with the synchronizing surfaces on said reverse andlow ratio countershaft gears, a positive clutching ring surrounding and splined shiftably to said synchronizing ring, said positive clutching ring being yieldably connected endwise to said'synchronizing ring and having clutch teeth for engagement selectively with the clutch teeth on said reverse and low ratio countershaft gears, a synchronizing ring shiftably splined on the countershaft rearwardly of said second ratio countershaft gear and having a synchronizing surface engageable with the synchronizing surface on said second ratio gear, and a positive clutching ring surrounding and splined shiftably to said last synchronizing ring, said last positive clutching ring being yieldingly connected endwise to said synchronizing ring and having clutch teeth for engagement with the clutch teeth on said second ratio countershaft gear.

3. A gear set' for motor vehicles having in combination a driving shaft, a driven shaft, bearing means near one end of said driven shaft and adapted to resist both axial and radial displacement of said driven shaft, a countershaft, meshing gears having helical teeth connecting the drive shaft and countershaft, a ratio gear also having helical teeth and fixed endwise on the driven shaft and against rotation with respect to said driven shaft, a roller bearing on the countershaft taking radial loads only, a ratio gear rotatable freely on said roller bearing and in constant meshing engagement with the ratio gear on the driven shaft, shiftable means on the countershaft for positively clutching said ratio countershaft gear to said countershaft and for freeing same therefrom, a bevel pinion on the driven shaft rearwardly of said ratio gear, and a diagonal take-off shaft having a bevel gear meshing with said bevel pinion, said first mentioned bearing means taking the thrust due to said helical gears and said bevel pinion and bevel gear.

4. A gear set for motor vehicles having -in combination a driving shaft, a driven shaft, a

countershaft, meshing gears connecting the drive shaft and countershaft, a ratio gear having helical teeth and fixed endwise on the drivenL shaft and against rotation with respect to said driven shaft, a roller bearing on the countershaft taking radial loads only, a, ratio gear also having helical teeth and rotatable freely on said roller bearing and in constant meshing engagement with the ratio gear on the,driven shaft, shiftable means on the countershaft for positively clutching said ratio countershaft gear to said countershaft and for freeing same therefrom, a bevel pinion on the driven shaft rearwardly of said ratio gear, a diagonal take-off shaft having -a bevel gear meshing with said bevel pinion, a case for said gear set, a roller bearing for the driven `shaft taking radial loads only and mounted in the rear wall of said case and between said ratio gear and said bevel pinion, and a bearing for said driven shaft rearwardiy -of said bevel pinion taking both radial and axial loads.

5. A gear set for motor vehicles having in combination an internal gear, a composite gear having external teeth meshing with the internal teeth of said internal gear, an overdrive member having external teeth meshing with the internal teeth on said composite gear, a driving shaft xed to said internal gear and extending through said internal gear, said composite gear and said overdrive member, a direct drive member on the extending end of said driving shaft, a coaxial driven shaft, a low ratio'- gear fixed on the driven shaft and having external teeth and internal splines inside and aligned with said external teeth, a clutching ring having constant splined engagement with the internal splines on said low ratio gear and shiftable into clutching engagement with said overdrive and direct drive members, a second ratio gear fixed endwise and against rotation with'respect to said driven shaft, a countershaft, meshing gears connecting the driven shaft and countershaft, low ratio and second ratio gears rotatable freely on the countershaft and in constant meshing engagement with the low ratio and second ratio gears on the driven shaft, and shiftable means on the countershaft for positively clutching said low ratio and second ratio countershaft gears to the countershaft and for freeing same therefrom.

6. A gear set for motor vehicles having in combination an internal gear, a composite gear having external teeth meshing with the internal teeth of said internal gear, an overdrive member having external teeth meshing with the internal teeth on said composite gear,'a driving shaft fixed to said internal gear and extending through said internal gear, said composite gear and said overdrive member, a direct drive member on the extending end of said driving shaft, a coaxial driven shaft, a low ratio gear'fixed on the driven shaft and having external teeth and internal splines inside and aligned with said external teeth, a clutching ring having constant splined engagement with the internal splines on said low ratio gear and shiftable into clutch engagement with said overdrive and direct drive members, a second ratiogear fixed against rotation with respect to said driven shaft, a countershaft, meshing gears connecting the driving shaft and countershaft, low ratio and second ratio gears rotatable freely on the countershaft and in constant meshing engagement with the low ratio and second ratio gears on the driven shaft, a reverse gear also rotatable freely on said countershaft, separate shiftable means on the countershaft for positively clutching said low ratio and second ratio countershaft gears tothe countershaft, and shiftable means also on the countershaft for positively clutching said reverse countershaft gear to the countershaft.A

7. In combination, a driving shaft, a driven.

shaft, a low ratio gear fixed on the driven shaft and having external teeth and internal splines inside and aligned with said teeth, internal gear overdrive and direct drive means between the driving shaft and driven shaft and including a shiftable clutch ring having external teeth in constant splined engagement with the internal splines on said low ratio gear and a set of internal teeth, an external gear mounted for rotation on said driving shaft and having a radially outwardly extending periphery with a set of 'teeth adapted to be engaged with said internal teeth. a composite gear having external teeth and internal teeth meshing with the external teeth of said external gear, and a gear member fixed to said driving shaft and having sets of internal and external gear teeth, the external teeth 'of said composite gear meshing with the internal teeth of said gear member, and means for driving said low ratio gear on the driven shaft from the external teeth on said gear member.

8. In combination, a relatively short gear case having a front wall and a rear wall, a driven shaft journaled in said rear wall, a driving shaft journaled in said front wall and extending into proximity to said rear wall and piloted in said driven shaft, a bearing cap secured to the rear wall of said case and having aligning means cooperating with said case, a countershaft, a ratio gear rotatable freely on said ,countershaft, synchronizing and positive clutch means on the countershaft for said ratio gear and in line with the rear wall of said case, and an end thrust bearing for the countershaft and carried by said bearing cap rearwardly of said synchronizing and positive clutch means. f

9. A gear set for motor vehicles having, in combination, an internaly gear, a driving shaft xed to said internal gear, a composite gear having external teeth meshing with the internal teeth of said internal gear, an overdrive member having external teeth meshing with the internal teeth on said composite gear, a direct drive member having a tubular portionv extending through said overdrive member and said composite gear and fixed to said driving shaft, and a driven shaft extending through said direct drive member and piloted in the driving shaft in line with said internal gear thereon.

10. A gear lset for motor hicles having, in combination, an internal gear, a driving shaft fixed to said internal, gear, a composite gear having external teeth meshing with the internal teeth of said internal gear, an overdrive member having external teeth meshing with the internal ternal gear thereon, needle-point bearings onY said driven shaft capable of taking radial loads only for rotatably supporting the adjacent end ofthedirectdrivememberthereomandathmst ring disposed between the rear end of said direct drive member and'said driven shaft.

l1.,A gear set for motor vehicles having,- inv combination, an internal gear, a driving shaft fixed to said internal gear, a composite gear having .external teeth meshing with l,the internal teeth of Asaid internal gear, an overdrive member having external teeth meshing with the internal teeth on said composite gear, a direct drive member having a tubular portion extending through said overdrive member and said composite gear and fixed to said driving shaft, a driven shaft extending through said direct drive member and .member capable of taking radial loads only for rotatably supporting the overdrive member thereon, means for transmitting axial thrust from said overdrive member to said direct drive m'ember, and means for transmitting axial thrustfrom said direct drive member to said driven shaft.

12. A gear set for motor vehicles having, in combination, an internal gear, a driving shaft fixed to said internal gear, a composite gear having external teeth meshing with the internal teeth of said internal gear,an overdrive member having external teeth' meshing with the internal` teeth on said composite gear and a radially outwardly extending flange, a thrust ringdisposed between said ilange and the rear face of said composite gear, a set of clutch teeth on said overdrive member rearwardly of said thrust ring, a direct drive member fixed to rotate with said driving shaft and having a set of clutch teeth at the rear end thereof, a thrust ring between the rear face of said direct drive member and said driven shaft, shiftable clutch means vdisposed between said two sets of clutch teeth and havingl a splined connection with said driven shaft, a third thrust ringl between the rear face of said overdrive member and the forward face of said direct drive member, and bearing means for-the rear end of said driven rshaft adapted to resist both radial and axial thrusts.

13. A gear set for motor vehicles having, in combination, an internal gear.l a driving shaft fixed to said internalgear, a composite gear having external teeth meshing with the internal teeth of said internal gear, an overdrive member having external teeth meshing with the internal teeth on said composite gear and a radially outwardly extendingf' ilange, a thrust ring disposed between said flange and the rear face of said vcomposite gear, a set of clutch teeth on said overdrivel member rearwardly of said thrust ring, a direct drive member xed to rotate` with said driving shaft and having a set of clutch teeth at the rear end thereof, a thrust ring between the rear face of said direct drive member and said driven shaft, shiftable clutch means disposed between said two sets of clutch teeth and having a splined connection with said driven shaft, and bearing means for the rear end of said driven shaft adapted to resist both radial and axial thrusts.

14. A gear set for `motor` vehicles having, in combination, an internal gear, a driving shaft fixed to said internal gear. a composite gear having external teeth meshing with the internal teeth of said internal gear, an overdrive member having external teeth meshing with the internal teethonsaidcompositegeanathrustbringdisposed between said overdrive member and said composite gear, a direct drive member xed to rotate with said driving shaft, thrust bearing means between said direct drive member and said overdrive member, thrust bearing means between said driving shaft and said driven shaft, said shafts being telescopically associated in coaxial relation and one of said shafts including a portion extending axially through said internal gear, composite gear, overdrive member, and direct drivemember, clutch mechanism adapted to optionally connect said driven shaft with either said overdrive member or said direct drive member, and bearing means for the rear end of said driven shaft adapted to resist both radial and axial thrusts.

THOMAS L. FAWICK. 

